EP0914552A1 - Vanne d'alimentation dosee en carburant volatilise - Google Patents

Vanne d'alimentation dosee en carburant volatilise

Info

Publication number
EP0914552A1
EP0914552A1 EP98912262A EP98912262A EP0914552A1 EP 0914552 A1 EP0914552 A1 EP 0914552A1 EP 98912262 A EP98912262 A EP 98912262A EP 98912262 A EP98912262 A EP 98912262A EP 0914552 A1 EP0914552 A1 EP 0914552A1
Authority
EP
European Patent Office
Prior art keywords
valve
section
nozzle
cross
valve seat
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP98912262A
Other languages
German (de)
English (en)
Other versions
EP0914552B1 (fr
Inventor
Erwin Krimmer
Wolfgang Schulz
Tilman Miehle
Manfred Zimmermann
Maria Esperilla
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0914552A1 publication Critical patent/EP0914552A1/fr
Application granted granted Critical
Publication of EP0914552B1 publication Critical patent/EP0914552B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M25/00—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture
    • F02M25/08—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture adding fuel vapours drawn from engine fuel reservoir
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M25/00—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture
    • F02M25/08—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture adding fuel vapours drawn from engine fuel reservoir
    • F02M25/0836—Arrangement of valves controlling the admission of fuel vapour to an engine, e.g. valve being disposed between fuel tank or absorption canister and intake manifold

Definitions

  • the invention relates to a valve for the metered introduction of fuel volatilized from a fuel tank of an internal combustion engine into an intake pipe of the internal combustion engine according to the preamble of claim 1.
  • a valve is already known (DE-PS 42 29 110) which has a valve seat , which is formed on an edge of an inlet cross-section of a Laval nozzle, against which a cylindrical valve member which can be actuated by an electromagnet bears in the closed position.
  • the valve seat thus also represents an axial delimitation of the Laval nozzle.
  • the design of the nozzle as a Laval nozzle enables a comparatively high flow rate to be achieved, so as to bring about only a relatively low flow resistance with a planned throughput of the valve.
  • valve according to the invention with the characterizing features of claim 1 has the advantage that even at high flow rates, only relatively low differential pressures are required at the valve. It is particularly advantageous that only a small valve lift is required to control the flow, so that a particularly fast-switching valve can be realized, in which only little scatter in the flow rate occurs.
  • a valve characteristic can advantageously be realized in which, depending on the differential pressure, there is a rapid increase in the flow characteristic for small differential pressures and a constant flow for larger differential pressures.
  • valve characteristic of the valve according to the invention can be changed in a simple manner.
  • FIG. 1 shows a Longitudinal section through the valve according to the invention
  • Figure 2 is a perspective view of a valve seat body of the valve according to a first embodiment
  • Figure 3 is a bottom view of a valve seat body of the valve according to a second embodiment.
  • the valve 1, shown schematically in longitudinal section in FIG. 1, serves for the metered introduction of fuel volatilized from a fuel tank of an internal combustion engine into an intake pipe of the internal combustion engine and is part of a fuel evaporation retention system, not shown in more detail, of a mixture-compressing, externally ignited internal combustion engine.
  • a fuel evaporation retention system not shown in more detail, of a mixture-compressing, externally ignited internal combustion engine.
  • the structure and function of such fuel evaporation restraint systems can be found, for example, on pages 48 and 49 of Bosch Technical Instruction, Motor Management Motronic, Second Edition, August 1993.
  • the structure and the mode of operation of such a valve 1, also referred to as a regeneration valve or tank ventilation valve are further known to the person skilled in the art from DE-OS 40 23 044, the disclosure of which is to be part of the present patent application.
  • the valve 1 has, coaxially to a longitudinal valve axis 2, a two-part valve housing with a cylindrically stepped, sleeve-shaped lower housing part 4 and a cover-shaped upper housing part 5.
  • the upper housing part 5 is, for example, placed on the lower housing part 4 and thereby encompasses the lower housing part 4 on its outer surface.
  • Both housing parts 4, 5 are preferably made of plastic and are, for example, inseparable, for example by means of ultrasonic welding or also separably connected, for example by means of a snap connection.
  • the lower housing part 4 carries an inlet connection 8 for connection to a ventilation connection, not shown, of a fuel tank of the internal combustion engine or to a downstream connection thereof
  • Adsorption filter The adsorption filter is used in a known manner for the intermediate storage of fuel vapor volatilized from the fuel tank and is filled with activated carbon, for example.
  • the upper housing part 5 has an outflow connection 9 for connection to an intake pipe of the internal combustion engine.
  • the inflow nozzle 8 and the outflow nozzle 9 are each arranged axially in the housing parts 4 and 5, approximately in alignment with one another.
  • An electromagnet 12 is arranged in the interior of the lower housing part 4. It has a pot-shaped magnet housing 14 with a coaxial, hollow-cylindrical magnet core 15 penetrating a bottom 25 of the magnet housing 14 and a cylindrical excitation coil 16, which is on a coil carrier
  • the magnetic core 15 has an axial through opening 21 which is delimited by the hollow magnetic core 15, so that fuel vapor can flow in the through opening 21 from the inflow nozzle 8 to the outflow nozzle 9.
  • the magnet housing 14 with the magnetic core 15 is inserted into the lower housing part 4 in such a way that 4 axial channels 24 remain between an outer jacket 22 of the magnet housing 14 and an inner wall 23 of the lower housing part 4, for example in the circumferential direction at the same angle are offset from one another, so that, as shown in FIG. 1, only two axial channels 24 can be seen, for example.
  • the axial channels 24 are located on the one hand in the lower housing part 4 between the bottom 25 of the magnet housing 14 and the inflow connector 8 annular space 27 on the one hand with the inflow connector 8 and on the other hand via bores 28 which are introduced into the magnet housing 14 near the open end of the magnet housing 14, in communication with the inside of the magnet housing 14 downstream of the excitation coil 16. Through these axial channels 24 can in the
  • Incoming fuel nozzle 8 also flow around the magnet housing 14 and thus dissipate the heat generated here.
  • the magnet housing 14 has a bent edge 29, which serves as a support flange for a bow-shaped valve seat body 31.
  • the valve seat body 31 forms the yoke of the electromagnet 12.
  • the valve seat body 31 partially covers the magnet housing 14 and is fastened to the lower housing part 4 by means of at least two fitting holes 47 shown in FIGS. 2 and 3.
  • the valve seat body 31 resting on the edge 29 is accommodated in an elastic, annular bearing receptacle 32 which has a U-shaped cross section and which in turn is clamped between the two housing parts 4 and 5.
  • a valve member 36 made of magnetic material also forms the armature of the electromagnet 12 and is fastened to a leaf spring 33 which is clamped on the edge side between the valve seat body 31 and the edge 29.
  • the valve seat body 31 has at least one valve opening 34.
  • two slit-shaped valve openings 34 are provided which, as shown in FIG. 2, have, for example, a semicircular shape and are provided opposite one another, so that they complement one another to form a fictitious circular shape.
  • FIG. 3 a top view of the valve seat body 31 designed according to a second embodiment, shows the valve openings 34 in a U-shape, which can be supplemented to form a fictitious rectangle.
  • the two valve openings 34 can be closed by the valve member 36, so that a double valve seat 37 results. As shown in FIG.
  • a through opening 38 running coaxially to the hollow cylindrical magnetic core 15 is provided in the valve member 36, through which fuel flowing from the inflow nozzle 8 via the through opening 21 of the magnetic core 15 can flow into the outflow nozzle 9 when the valve openings 34 are open.
  • the valve member 36 is acted upon by a valve closing spring 43 in the valve closing direction in the direction of the outflow connector 9, which is supported on the one hand on the valve member 36 and on the other hand on a sleeve-shaped end 41 of the magnetic core 15.
  • the valve member 36 carries on its side facing the valve double seat 37 a sealing rubber 42 made of elastic
  • the sealing rubber 42 also lines the through opening 38 and projects somewhat beyond a side of the valve member 36 facing away from the valve double seat 37.
  • the valve closing spring 43 presses the valve member 36 with the sealing rubber 42 onto the valve double seat 37 and thus closes the valve openings 34.
  • the valve member 36 with its sealing rubber 42 protruding from the through opening 38 becomes against the end 41 of the magnetic core 15 pressed, which forms a stop 44 for the attractive movement of the valve member 36.
  • the stop 44 can be axially displaced and thereby the flow rate with the valve member 36 lifted from the valve double seat 37 at the maximum.
  • the valve closing spring 43 is weakly dimensioned since, in the event of a pressure drop between the outlet connection 9 and the inlet connection 8, a suction effect is exerted on the valve member 36 in the direction of valve closing and the closing effect of the valve closing spring 43 is supported.
  • the electromagnet 12 is actuated in a clocked manner by the control electronics of a control device (not shown in more detail), for which purpose a connector connection 50 is provided on the upper housing part 5.
  • the cycle rate is predetermined by the operating state of the internal combustion engine, so that the flow rate of volatilized fuel vapor passing through valve openings 34 from the inflow nozzle 8 into the outflow nozzle 9 can be dosed accordingly.
  • the channel penetrating the outflow nozzle 9 is designed in the form of a Laval nozzle 55, which is composed in a known manner from a convergent part 56 and a divergent part 57.
  • the Laval nozzle 55 tapers from a first inlet cross section 60 downstream in the vicinity of the valve seat body 31 to a narrowest cross section 61, in order to then widen from the narrowest cross section 61 to an end cross section 62 at the downstream end.
  • the cross sections 60, 61, 62 are designed in such a way that the inlet cross section 60 is at least equal to or larger than the end cross section 62.
  • the inlet cross section 60 is preferably 1.1 to 2 times larger than the end cross section 62.
  • the narrowest cross section 61 is preferably 2 up to 4 times smaller than that Entry cross section 60.
  • the length of the Laval nozzle 55 measured is, for example, 3 to 5 times larger than a diameter at the inlet cross-section 60.
  • the side 49 of the valve seat body 31 is at a distance from the inlet side of the outflow connector 9 having the inlet cross-section 60 in the direction of the valve longitudinal axis 2, so that an intermediate space 63 is formed between the side 49, the inlet side of the outflow connector 9 and the sealing ring 51, which has at least one lateral extension perpendicular to the longitudinal axis 2 of the valve, which is as large as the diameter of the inlet cross-section 60, and into which the valve openings 34 flow out. Since only the two valve openings 34 of the valve seat body 31 have to be covered by the valve member 36 for actuation, it is possible to optimally adjust the valve cross section of the valve member 36 by simply changing the valve lift
  • Valve openings 34 are made substantially smaller from an inlet cross-section 60 of the Laval nozzle 55. Both cross-sections together are preferably only about 10 to 20 percent of the inlet cross-section 60. Due to the relatively no cross-section of both valve openings 34, the interruption of the fuel flow by means of valve member 36 can be high Speed are carried out so that a particularly fast switching valve 1 can be realized.
  • the adaptation to the desired flow rates of the valve 1 is possible by simply changing the valve stroke or by rotating the magnetic core 15 in the magnet housing 14.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

Les types connus de vanne de dégazage de réservoir qui ont une tuyère de Laval, posent le problème de la régulation fine du débit du fait que la section d'entrée de la tuyère est directement recouverte d'un élément de vanne. La présente invention porte sur une vanne dont le siège (37) fait corps avec le support de vanne (31), lequel présente au moins une ouverture (34) pouvant être fermée par ledit siège-support (36). La section de ladite ouverture (34) est sensiblement inférieure à la section d'entrée (60) de la tuyère de Laval (55), ladite section d'entrée étant montée à l'ouverture, avec un espacement. La vanne selon l'invention est conçue pour permettre l'amenée dosée de carburant d'un réservoir de moteur à combustion interne à compression de mélange et à allumage par étincelle dans une tubulure d'admission dudit moteur.
EP98912262A 1997-05-23 1998-02-18 Vanne d'alimentation dosee en carburant volatilise Expired - Lifetime EP0914552B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19721562A DE19721562A1 (de) 1997-05-23 1997-05-23 Ventil zum dosierten Einleiten von verflüchtigtem Brennstoff
DE19721562 1997-05-23
PCT/DE1998/000472 WO1998053195A1 (fr) 1997-05-23 1998-02-18 Vanne d'alimentation dosee en carburant volatilise

Publications (2)

Publication Number Publication Date
EP0914552A1 true EP0914552A1 (fr) 1999-05-12
EP0914552B1 EP0914552B1 (fr) 2003-05-07

Family

ID=7830256

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98912262A Expired - Lifetime EP0914552B1 (fr) 1997-05-23 1998-02-18 Vanne d'alimentation dosee en carburant volatilise

Country Status (8)

Country Link
US (1) US6149126A (fr)
EP (1) EP0914552B1 (fr)
JP (1) JP2000515606A (fr)
KR (1) KR20000029436A (fr)
BR (1) BR9804944A (fr)
DE (2) DE19721562A1 (fr)
RU (1) RU2195571C2 (fr)
WO (1) WO1998053195A1 (fr)

Families Citing this family (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19839476A1 (de) * 1998-08-29 2000-03-02 Bosch Gmbh Robert Ventil zum dosierten Einleiten von verflüchtigtem Brennstoff
FR2788324A1 (fr) * 1999-01-08 2000-07-13 Sagem Siege de clapet d'electrovanne
DE19901090A1 (de) * 1999-01-14 2000-07-20 Bosch Gmbh Robert Ventil zum dosierten Einleiten von verflüchtigtem Brennstoff
WO2000075502A1 (fr) * 1999-06-08 2000-12-14 Sagem Electrovanne de purge pour dispositif d'evacuation de vapeurs
DE19928207A1 (de) * 1999-06-19 2000-12-21 Bosch Gmbh Robert Magnetventil
DE19935261A1 (de) * 1999-07-27 2001-02-01 Bosch Gmbh Robert Ventil zum dosierten Einleiten von verflüchtigtem Brennstoff in einen Ansaugkanal einer Brennkraftmaschine
ES2167275B1 (es) * 2000-10-20 2003-10-16 Bitron Ind Espana Sa Electrovalvula reguladora de caudal de aire.
US6450152B1 (en) * 2001-06-15 2002-09-17 Siemens Automotive Inc. Low-profile fuel tank isolation valve
DE10156231C1 (de) * 2001-11-15 2003-04-30 Freudenberg Carl Kg Ventil
US7086383B2 (en) * 2003-04-04 2006-08-08 Siemens Vdo Automotive Inc. Permanent magnet digital purge valve
WO2004113712A2 (fr) * 2003-06-20 2004-12-29 Siemens Vdo Automotive Inc. Vanne de purge comprenant un actionneur a aimant permanent
JP2005155712A (ja) * 2003-11-21 2005-06-16 Mitsubishi Electric Corp 電磁弁
DE10360773A1 (de) * 2003-12-23 2005-07-28 Robert Bosch Gmbh Brennstoffeinspritzventil
CN1295431C (zh) * 2004-01-02 2007-01-17 沈开华 发动机多功能数码滤清器
GB0503098D0 (en) * 2005-02-15 2005-03-23 Reckitt Benckiser Uk Ltd Spray device
GB0503095D0 (en) * 2005-02-15 2005-03-23 Reckitt Benckiser Uk Ltd Holder
WO2006087516A1 (fr) * 2005-02-15 2006-08-24 Reckitt Benckiser (Uk) Limited Ensemble joint d'etancheite pour contenant sous pression
GB0521063D0 (en) * 2005-10-18 2005-11-23 Reckitt Benckiser Uk Ltd Spraying device
JP4166779B2 (ja) * 2005-11-28 2008-10-15 三菱電機株式会社 内燃機関制御装置
US20080000456A1 (en) * 2006-06-30 2008-01-03 Siemens Canada Limited Cost-optimized canister purge valve
GB0623052D0 (en) * 2006-11-18 2006-12-27 Reckitt Benckiser Uk Ltd An assembly
JP5414088B2 (ja) * 2008-06-17 2014-02-12 サンデン株式会社 圧縮機
CN201363474Y (zh) * 2009-02-20 2009-12-16 厦门科际精密器材有限公司 一种结构改进的电磁线性阀
JP6176215B2 (ja) * 2014-09-25 2017-08-09 株式会社デンソー 二段切替弁
JP7358038B2 (ja) * 2018-07-18 2023-10-10 株式会社ミクニ 電磁弁
US12404948B2 (en) * 2022-11-24 2025-09-02 Hydrotek Corporation Solenoid valve

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DE3519292A1 (de) * 1985-05-30 1986-12-04 Robert Bosch Gmbh, 7000 Stuttgart Abgabeanlage zur einleitung von verfluechtigtem kraftstoff in eine brennkraftmaschine
JPS62110087A (ja) * 1985-11-06 1987-05-21 Aisin Seiki Co Ltd 切替弁装置
DE3802664C1 (fr) * 1988-01-29 1988-10-13 Fa. Carl Freudenberg, 6940 Weinheim, De
DE3844453C2 (de) * 1988-12-31 1996-11-28 Bosch Gmbh Robert Ventil zum dosierten Zumischen von verflüchtigtem Kraftstoff zum Kraftstoffluftgemisch einer Brennkraftmaschine
DE4023044A1 (de) * 1990-07-20 1992-01-23 Bosch Gmbh Robert Ventil zum dosierten zumischen von verfluechtigtem kraftstoff zum kraftstoffluftgemisch einer brennkraftmaschine
US5188141A (en) * 1991-12-03 1993-02-23 Siemens Automotive Limited Vacuum boost valve
DE4139946C1 (fr) * 1991-12-04 1993-02-04 Fa. Carl Freudenberg, 6940 Weinheim, De
DE4229110C1 (de) * 1992-09-01 1993-10-07 Freudenberg Carl Fa Vorrichtung zum vorübergehenden Speichern und dosierten Einspeisen von im Freiraum einer Tankanlage befindlichen flüchtigen Kraftstoffbestandteilen in das Ansaugrohr einer Verbrennungskraftmaschine
DE4244113A1 (de) * 1992-12-24 1994-06-30 Bosch Gmbh Robert Ventil zum dosierten Einleiten von verflüchtigtem Brennstoff in einen Ansaugkanal einer Brennkraftmaschine
US5630403A (en) * 1996-06-13 1997-05-20 Siemens Electric Limited Force-balanced sonic flow emission control valve

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Also Published As

Publication number Publication date
EP0914552B1 (fr) 2003-05-07
KR20000029436A (ko) 2000-05-25
US6149126A (en) 2000-11-21
BR9804944A (pt) 1999-08-24
DE19721562A1 (de) 1998-11-26
RU2195571C2 (ru) 2002-12-27
DE59808243D1 (de) 2003-06-12
WO1998053195A1 (fr) 1998-11-26
JP2000515606A (ja) 2000-11-21

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